JPH0245642A - Piston of internal combustion engine - Google Patents
Piston of internal combustion engineInfo
- Publication number
- JPH0245642A JPH0245642A JP63196150A JP19615088A JPH0245642A JP H0245642 A JPH0245642 A JP H0245642A JP 63196150 A JP63196150 A JP 63196150A JP 19615088 A JP19615088 A JP 19615088A JP H0245642 A JPH0245642 A JP H0245642A
- Authority
- JP
- Japan
- Prior art keywords
- boss
- piston
- oil groove
- pin
- insertion hole
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 8
- 230000037431 insertion Effects 0.000 claims abstract description 24
- 238000003780 insertion Methods 0.000 claims abstract description 24
- 238000005299 abrasion Methods 0.000 abstract 2
- 239000003921 oil Substances 0.000 description 19
- 239000010687 lubricating oil Substances 0.000 description 2
- 230000036772 blood pressure Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 231100000241 scar Toxicity 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J1/00—Pistons; Trunk pistons; Plungers
- F16J1/10—Connection to driving members
- F16J1/14—Connection to driving members with connecting-rods, i.e. pivotal connections
- F16J1/16—Connection to driving members with connecting-rods, i.e. pivotal connections with gudgeon-pin; Gudgeon-pins
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F2200/00—Manufacturing
- F02F2200/04—Forging of engine parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
- F05C2201/00—Metals
- F05C2201/02—Light metals
- F05C2201/021—Aluminium
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Description
【発明の詳細な説明】
［＆梁上の利用分野］
本発明は船外機用内燃機関等に用いて好適なピストンに
関する。DETAILED DESCRIPTION OF THE INVENTION [Fields of use on beams] The present invention relates to a piston suitable for use in internal combustion engines for outboard motors and the like.
［従来の技術］
従来の内燃機関のピストンは、第５図に示す如く、ピン
ボス部ｌの連接棒大端部と摺接するボス端面２に、該ピ
ンボス部ｌのピン挿入孔３を反ピストンヘッド側に開放
する油溝４を設けている。[Prior Art] As shown in FIG. 5, in a conventional piston for an internal combustion engine, a pin insertion hole 3 of a pin boss l is placed in a boss end surface 2 that slides in contact with a large end of a connecting rod of a pin boss l, and a pin insertion hole 3 of the pin boss l is placed in a position opposite to the piston head. An oil groove 4 that opens to the side is provided.
この油ｊｔｌ！ ４は、クランク室内に浮遊する混合気
中の潤滑油やクランク軸がかき上げる潤滑油を、■ピス
トンピンとピンボス部のピン挿入孔との摺接領域、ある
いは■連接棒大端部とピンボス部のボス端面との摺接領
域に導き入れ、結果としてそれら■、■の摺接部を潤滑
および冷却する。This oil jtl! 4 removes the lubricating oil in the air-fuel mixture floating in the crank chamber and the lubricating oil scraped up by the crankshaft from ■ the sliding contact area between the piston pin and the pin insertion hole of the pin boss, or ■ the large end of the connecting rod and the pin boss. It is introduced into the sliding contact area with the end face of the boss, and as a result, the sliding contact parts (1) and (2) are lubricated and cooled.
［発明が解決しようとする課題１
しかしながら、上記従来のピストンにあっては、油溝４
を設けるにあたり、ボス端面２を反ピストンヘッド側の
外径部からピン挿入孔３の直径部を含む範囲にわたり斜
面状にカットする如くしている。[Problem to be Solved by the Invention 1] However, in the above conventional piston, the oil groove 4
In providing this, the boss end face 2 is cut in a slope shape over a range including the outer diameter part on the side opposite to the piston head and the diameter part of the pin insertion hole 3.
このため、従来のピストンにあっては、ボス端面２にお
いて、現実に連接棒大端部と摺接する実効端面２Ａは第
６図に示す如くの半円状のみとなる。Therefore, in the conventional piston, the effective end surface 2A of the boss end surface 2, which actually makes sliding contact with the large end of the connecting rod, is only semicircular as shown in FIG.
このことは、ボス端面２と連接棒大端部との間に生ずる
スラストに対する受は面積が過小となることを意味し、
ボス端面２に作用する面圧が大きくなり、ボス端面２が
摩耗しやすい状況あることを意味する。This means that the area of the support for the thrust generated between the boss end face 2 and the large end of the connecting rod is too small.
This means that there is a situation where the surface pressure acting on the boss end face 2 becomes large and the boss end face 2 is likely to wear out.
特に、船外機用内燃機関におけるように、機関のクラン
ク軸が鉛直配置される場合には、クランク軸と平行に配
設されているピストンピンモ鉛直配置され、連接棒重量
が直接的にボス端面２に及ぶから、ボス端面２の実効面
積（実効端面２Ａの面積）の増大化は重要である。In particular, when the crankshaft of the engine is arranged vertically, such as in an internal combustion engine for an outboard motor, the piston pin, which is arranged parallel to the crankshaft, is arranged vertically, and the weight of the connecting rod is directly applied to the boss end face. Therefore, it is important to increase the effective area of the boss end face 2 (the area of the effective end face 2A).
本発明は、油溝がピンボス部のピン挿入孔を反ピストン
ヘッド側に開放する開放面積を確保しながら、ボス端面
の実効面積を増大化することを目的とする。An object of the present invention is to increase the effective area of the boss end face while ensuring an open area in which the oil groove opens the pin insertion hole of the pin boss portion to the side opposite to the piston head.
［課題を解決するための手段］
本発明は、ピンボス部の連接棒大端部と摺接するボス端
面に、該ピンボス部のピン挿入孔を反ピストンヘッド部
側に開放する油溝を凹設してなる内燃機関のピストンに
おいて、油溝は、ボス端面における凹設幅をピン挿入孔
径と同等以下に設定され、かつピストンの中心軸に略平
行をなす溝面にてａｔされるようにしたものである。[Means for Solving the Problems] The present invention includes an oil groove that opens the pin insertion hole of the pin boss part to the side opposite to the piston head part, in the boss end surface that makes sliding contact with the large end of the connecting rod of the pin boss part. In a piston for an internal combustion engine, the oil groove has a concave width on the end face of the boss equal to or smaller than the diameter of the pin insertion hole, and is located on a groove surface that is approximately parallel to the central axis of the piston. It is.
［作用］
本発明によれば、「油溝を、ピストンの中心軸に略平行
をなす溝面にて構成すること」とした。[Operation] According to the present invention, "the oil groove is constituted by a groove surface that is substantially parallel to the central axis of the piston."
したがって、その凹設範囲を、「ボス端面における凹設
幅がピン挿入孔径と同等以下」という条件内で、ボス端
面の幅方向およびこれと直交する方向（ピン挿入孔の軸
方向）に関して適宜設定することにより、油溝がピンボ
スのピン挿入孔を反ピストンヘッド側に開放する必要十
分な開放面積を確保できる。Therefore, the range of the recess is set appropriately in the width direction of the boss end face and the direction perpendicular thereto (the axial direction of the pin insertion hole) within the condition that "the width of the recess on the boss end face is equal to or less than the diameter of the pin insertion hole". By doing so, it is possible to secure a necessary and sufficient opening area for the oil groove to open the pin insertion hole of the pin boss on the side opposite to the piston head.
また、「油溝のボス端面における凹設幅はピン挿入孔径
と同等以下に設定される」から、ボス端面が現実に連接
棒大端部と摺接する実効端面は前述した従来の半円状か
ら略Ｕ字状に拡張せしめられ、その実効面積を増大化で
きる。In addition, since "the width of the recess on the boss end face of the oil groove is set to be equal to or less than the diameter of the pin insertion hole," the effective end face where the boss end face actually makes sliding contact with the large end of the connecting rod is different from the conventional semicircular shape mentioned above. It is expanded into a substantially U-shape, and its effective area can be increased.
［実施例］
第１図は本発明の一実施例に係るピストンを示す断面図
、第２図は第１図のＩＩ −ＩＩ線に沿う断面図、第３
図は第１図の底面図、第４図は第１図のＩＶ−ＩＶ線の
ボス端面を示す端面図である。[Example] Fig. 1 is a sectional view showing a piston according to an embodiment of the present invention, Fig. 2 is a sectional view taken along line II-II in Fig. 1, and Fig.
The figure is a bottom view of FIG. 1, and FIG. 4 is an end view showing the end face of the boss taken along line IV--IV in FIG. 1.
ピストン１０は、ピストンヘッド部１１、ピストンリン
グ部１２、ピンボス部１３、およびスカ−）部１４から
形成されている。The piston 10 is formed from a piston head part 11, a piston ring part 12, a pin boss part 13, and a scar part 14.
ピストン１０は、ピンボス部１３の連接棒大端部１５と
摺接するボス端面１６に、該ピンボス部１３のピン挿入
孔１７を反ピストンヘッド部側に開放する油溝１８を凹
設している。The piston 10 has an oil groove 18 formed in a boss end surface 16 that slides in contact with the connecting rod large end 15 of the pin boss 13 to open the pin insertion hole 17 of the pin boss 13 toward the side opposite to the piston head.
油溝１８は、ボス端面１６における凹設置！ＩＩＩｗを
°、ピン挿入孔径ｄと同等以下に設定されている（第２
図参照）、また、油溝１８は、ピストン１０の中心軸１
０ｃに略平行をなすＲ状溝面１９にて構成されている。The oil groove 18 is installed in a recess on the boss end face 16! IIIw is set equal to or smaller than the pin insertion hole diameter d (second
), and the oil groove 18 is connected to the central axis 1 of the piston 10.
It is composed of an R-shaped groove surface 19 that is approximately parallel to 0c.
なお、油溝１８は、具体的にはエンドミル等のカッタ２
ｏにて形成される（第３図参照）。Note that the oil groove 18 is specifically used for a cutter 2 such as an end mill.
o (see Figure 3).
次に、上記実施例の作用について説明する。Next, the operation of the above embodiment will be explained.
上記実施例によれば、「油溝１８を、ピストン１０の中
心軸１０ｃに略平行をなす溝面にて構成すること」とし
た、したがって、その凹設範囲を、「ボス端面１６にお
ける凹設幅Ｗがピン挿入孔径ｄと同等以下」という条件
内で、ボス端面１６の幅方向およびこれに直交する方向
（ピン挿入孔１７の軸方向）に関して適宜設定すること
により、油溝１８がピンボス部１３のピン挿入孔１７を
反ピストンヘッド側に開放する必要十分な開放面積を確
保できる。According to the above embodiment, "the oil groove 18 is constituted by a groove surface that is substantially parallel to the central axis 10c of the piston 10," and therefore, the recessed range is defined as "the recessed area on the boss end face 16." By appropriately setting the width direction of the boss end face 16 and the direction perpendicular thereto (the axial direction of the pin insertion hole 17) within the condition that the width W is equal to or smaller than the pin insertion hole diameter d, the oil groove 18 is formed in the pin boss portion. A necessary and sufficient open area for opening the 13 pin insertion holes 17 on the side opposite to the piston head can be secured.
また、「油溝１８のボス端面１６における凹設幅Ｗはピ
ン挿入孔径ｄと同等以下に設定される」から、ボス端面
１６が現実に連接棒大端部１５と摺接する実効端面１．
６Ａは、前述した従来の半円状から略Ｕ字状に拡張せし
められ、その実効面積を増大化できる。Furthermore, since "the recessed width W of the oil groove 18 on the boss end surface 16 is set to be equal to or smaller than the pin insertion hole diameter d", the effective end surface 1.
6A is expanded from the conventional semicircular shape described above to a substantially U-shape, and its effective area can be increased.
このことは、ボス端面１６と連接棒大端部１５との間に
生ずるスラストに対する受面積を確保し、船外機用内燃
機関におけるように機関のクランク軸が鉛直配置され、
前述の如く連接棒重量が直接的にボス端面１６に及ぶ場
合にも、上記ボス端面１６の実効面積の増大化によりボ
ス端面１６に生ずる血圧を軽減してボス端面１６の摩耗
を抑制できることを意味する。This ensures a receiving area for the thrust generated between the boss end face 16 and the connecting rod large end 15, and allows the crankshaft of the engine to be arranged vertically as in an internal combustion engine for an outboard motor.
This means that even when the weight of the connecting rod is directly applied to the boss end face 16 as described above, the increase in the effective area of the boss end face 16 reduces the blood pressure generated on the boss end face 16 and suppresses wear of the boss end face 16. do.
なお、本発明の実施において、油溝の溝面は必ずしもＲ
状でなく、第３図に鎖線にて示す如く全体矩形状をなす
等であってもよい。Note that in carrying out the present invention, the groove surface of the oil groove is not necessarily R.
Instead of a shape, it may have an overall rectangular shape as shown by the chain line in FIG.
以上のように本発明によれば、油溝がピンボス部のピン
挿入孔を反ピストンヘッド側に開放する開放面積を確保
しながら、ボス端面の実効面積を増大化できる。As described above, according to the present invention, the effective area of the boss end face can be increased while ensuring an open area where the oil groove opens the pin insertion hole of the pin boss portion toward the side opposite to the piston head.
第１図は本発明の一実施例に係るピストンを示す断面図
、第２図は第１図のＩＩ −Ｈ線に沿う断面図、第３図
は第１図の底面図、第４図は第１図の■−ＩＶ線のボス
端面を示す端面図、第５図は従来例に係るピストンを示
す断面図、第６図は第５図のＶＩ−ＶＩ線に沿う端面図
である。
ｌＯ・・・ピストン、
１０ｃ・・・中心軸、
１３・・・ピンボス部、
１５・・・連接棒大端部、
１６・・・ボス端面、
１７・・・ピン挿入孔、
１８・・・油溝、
１９・・・溝面、
Ｗ・・・凹設幅、
ｄ・・・ピン挿入孔径。FIG. 1 is a sectional view showing a piston according to an embodiment of the present invention, FIG. 2 is a sectional view taken along line II-H in FIG. 1, FIG. 3 is a bottom view of FIG. 1, and FIG. 1, FIG. 5 is a sectional view showing a piston according to a conventional example, and FIG. 6 is an end view taken along line VI-VI in FIG. 5. lO... Piston, 10c... Central shaft, 13... Pin boss portion, 15... Connecting rod large end, 16... Boss end surface, 17... Pin insertion hole, 18... Oil Groove, 19...Groove surface, W...Concave width, d...Pin insertion hole diameter.
Claims (1)
、該ピンボス部のピン挿入孔を反ピストンヘッド部側に
開放する油溝を凹設してなる内燃機関のピストンにおい
て、油溝は、ボス端面における凹設幅をピン挿入孔径と
同等以下に設定され、かつピストンの中心軸に略平行を
なす溝面にて構成されることを特徴とする内燃機関のピ
ストン。(1) In a piston for an internal combustion engine, an oil groove is provided in the end face of the boss that slides with the large end of the connecting rod of the pin boss to open the pin insertion hole of the pin boss to the side opposite to the piston head. A piston for an internal combustion engine, characterized in that the width of the recess on the end face of the boss is set to be equal to or smaller than the diameter of the pin insertion hole, and the piston is formed of a groove surface that is substantially parallel to the central axis of the piston.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63196150A JPH0245642A (en) | 1988-08-08 | 1988-08-08 | Piston of internal combustion engine |
| US07/390,660 US4969433A (en) | 1988-08-08 | 1989-08-07 | Piston for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP63196150A JPH0245642A (en) | 1988-08-08 | 1988-08-08 | Piston of internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0245642A true JPH0245642A (en) | 1990-02-15 |
Family
ID=16353042
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP63196150A Pending JPH0245642A (en) | 1988-08-08 | 1988-08-08 | Piston of internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| US (1) | US4969433A (en) |
| JP (1) | JPH0245642A (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5239955A (en) * | 1993-01-07 | 1993-08-31 | Ford Motor Company | Low friction reciprocating piston assembly |
| DE19943945A1 (en) * | 1999-09-14 | 2001-03-22 | Federal Mogul Wiesbaden Gmbh | Piston head |
| DE10340292A1 (en) * | 2003-09-02 | 2005-04-14 | Mahle Gmbh | Piston for an internal combustion engine |
| US10352270B2 (en) | 2016-03-01 | 2019-07-16 | Tenneco Inc. | Galleryless piston with connection to pockets |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS621490U (en) * | 1985-06-18 | 1987-01-07 |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2742883A (en) * | 1953-07-15 | 1956-04-24 | Frank J Smith | Oil cooled piston structure |
| US3204617A (en) * | 1963-12-09 | 1965-09-07 | Continental Aviat & Eng Corp | Piston assembly |
| US3613521A (en) * | 1968-11-07 | 1971-10-19 | Komatsu Mfg Co Ltd | Piston for internal combustion engine |
| FR2238372A5 (en) * | 1973-07-19 | 1975-02-14 | Dampers | |
| US4013057A (en) * | 1975-05-14 | 1977-03-22 | Dana Corporation | Piston assembly |
| US4026197A (en) * | 1975-06-02 | 1977-05-31 | Caterpillar Tractor Co. | Oil cooled piston rings |
| DE2543478C2 (en) * | 1975-09-30 | 1983-01-05 | Günter 8543 Hilpoltstein Elsbett | Pistons for internal combustion engines, especially diesel engines |
| US4342291A (en) * | 1980-01-16 | 1982-08-03 | Lewis William C | Expandable piston motor |
| US4517930A (en) * | 1982-09-28 | 1985-05-21 | Kawasaki Jukogyo Kabushiki Kaisha | Piston of combustion engine |
| US4644853A (en) * | 1984-11-23 | 1987-02-24 | General Motors Corporation | Piston and bearing assemblies |
-
1988
- 1988-08-08 JP JP63196150A patent/JPH0245642A/en active Pending
-
1989
- 1989-08-07 US US07/390,660 patent/US4969433A/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS621490U (en) * | 1985-06-18 | 1987-01-07 |
Also Published As
| Publication number | Publication date |
|---|---|
| US4969433A (en) | 1990-11-13 |
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